Peripheral closed chamber engine



March 5@, 1965 T. 1.. GLENN 3,175,360

PERIPHERAL CLOSED CHAMBER ENGINE Filed Jan. 3, 1961 2 Sheets-Sheet l IOe F larch 3Q, 1965 PERIPHERAL CLOSED CHAMBER ENGINE Filed Jan. 3. 1961 T. L. GLENN i l 5 IO! 2 Sheets-Sheet 2 United States Patent 3,175,366 PERHHERAL CLQSED CHAMBER ENGINE Thomas Lane Glenn, Loclmey, Tex. Filed Jan. 3, 1961, Ser. No. 80,083 3 Claims. (Cl. 60--39.61)

This invention relates to engines for developing rotation from energy of expansible gases and more particularly to an engine in which forces developed upon the expansion of gases are applied tangentially to a rotating cyilnder.

In internal combusion engines and steam engines of the piston type, forces are produced which are applied to a crankshaft upon the displacement of a piston in a cylinder. Combustible mixtures of gases are fired after compression and move the piston during a work cycle. The energy produced during the work cycle is transferred from the piston through a connecting rod to a crankshaft. The full mechanical advantage of force thus developed cannot be realized until the crankshaft is at a right angle to the stroke of the piston or at approximately half way of the completed power stroke. Furthermore, energy is lost in the rapid change in direction of the reci rocating pistons. On the other hand, in internal combustion engines of the turbine type tangentially directed forces are developed in an open chamber upon expansion to move the rotor.

The present invention embodies a combination of features useful in internal combusion engines having reciprocating pistons and turbine engines where tangentially directed forces are produced. It is therefore an object of the present invention to provide an engine which com bines the properties of a turbine type engine and a reciprocating piston type engine. It is a further object of the invention to provide for the ignition and expansion of a gas in a closed peripheral zone for the development of a tangentially directed force on a rotating cylinder which forms at least a part of the wall surrounding such zone.

More particularly in accordance with the present invention, there is provided an engine in which a housing is characterized by a cylindrical bore and in which a rotor is mounted coaxially in the housing and adapted to engage the walls of the cylindrical bore at axially spaced peripheral zones to form an annular chamber between the wall of the bore and the outer surface of the rotor. A pair of stops tranversely oriented in the annular chamber form closures therefor. One of the stops is carried by the rotor and the other of the stops is mounted on the housing. Means is provided for cylically injecting an expanding gas mixture into the annular chamber between the stops for developing tangentially directed forces on the stops to move the rotor relative to the housing. A means operable in synchronism with rotation of the rotor is provided for retracting at least one of the stops to permit the stops to pass one another. The rotor is then connected to an output shaft for delivering work to the shaft resulting from the expansion of the gases in the annular chamber.

In accordance with one embodiment the invention there is provided an internal combustion engine of the type above described wherein ring like sealing means encircle a rotor to form an annular chamber between the exterior of the rotor and the inner wall of the cylindrical housing. At lea-st one radially aligned cylinder is mounted in the rotor and has a piston coupled by a connecting rod to a crankshaft which is fixed with respect to said cylindrical housing at an axis which is eccentric with respect to the axis of the cylindrical bore. Means are provided for injecting a combustible gas mixture into the cylinder with the valve means then being operable by reason of the eccentric axis for its crankshaft cyclically to deliver compressed gases into the annular chamber between the stops a 3,175,350 Ice Patented Mar. 39, 1965 on the rotor which upon firing expands to propel one of the stops away from the other.

For a more complete understanding of the present in vention and for further objects and advantages thereof, reference may now be had to the following description taken in conjunction with the accompanying drawings in which? PEG. 1 is a sectional view of a motor constructed in accordance with the present invention taken along the lines 11 of FIG. 2;

FIG. 2 is a view partially in section of the system of FIG. 1 taken along the lines 22 of FIG. 1;

FIG. 3 is an enlarged view of the top of the piston of FIG. 2;

FIG. 4 is a partial sectional view taken along the lines 4-4 of FIG. 2;

FIG. 5 illustrates in a sectional view a modification of a dual rotor system together with means for delivering combustible gases to an expansion chamber;

FIG. 6 is an external view of a modification of the invention shown partially in section;

FIG. 7 is a detailed view of a valve operator taken along the lines 77 of FIG. 6;

FIG. 8 is a view of a modification of the invention having an external compression unit; and

FIG. 9 is an enlarged View showing a modified valve for a mechanism such as shown in FIG. 8.

Referring now to FIGS. 1 and 2, an internal combusion engine is shown partially in section with housing 10 formed by relatively short cylinder having an internal bore in which there is positioned a rotor 11. Rotor 11 is mounted for rotation about a center axis 12. As best seen in FIG. 2, the rotor 11 is mounted on peripheral bearings 13 and 14. The rotor 11 has a hollow center and has a pair of internal gears 15 and 16, the gear 15 being seen in FIG. 1. Gear 15 meshes with a gear 17 mounted on shaft 18 which in turn is connected to a gear 19 which meshes with a gear 20 mounted on a shaft 21 whose axis coincides with axis 12 of the bore of housing it). In a similar manner, the gear 16 at the left hand side of the engine as viewed in FIG. 2 engages a pinion 24 which is mounted on a shaft 25. Shaft 25 carries a pinion 25 which meshes with a pinion 27, the latter being mounted on a shaft 2 8. Shafts 21 and 23 preferably are coaxially aligned with the axis 12 of the bore of housing 10. The shafts 2'1 and 28 do not extend through the bore of housing it} but merely into it, being supported by end closure plates 3i and 31 located respectively on the right and left ends of the housing 10 as shown in FIG. 2.

With the system thus far described, the rotor 11 upon rotation relative to housing 10 will transmit rotary motion through gears 15 and 16 which ultimately is delivered from the engine by way of shafts 21 and 2-8. It is to be noted that shafts l8 and 25, 21 and 28 are supported by the end plates 3% and 31 of the housing 10.

Referring again to FIGS. 1 and 2, it will be seen particularly in PEG. 2 that the outer surface of the rotor 11 is recessed to form an annular expansion chamber 35. A stop 36 having an end shaped in accordance with the cross sectional area of the annular chamber extends through a slot 37 in the wall of housing .10 and into contact with the surfaces of the rotor 11 and thus forms a first closure member for chamber 35. The expansion chamber 35 in the form illustrated has a cross section of the form of an inverted, truncated triangle having equal angles at the base thereof. The stop 36 thus provides a closure for the expansion chamber 35. The stop 36 normally is maintained in a closed position, extending into the chamber 35 and into engagement with the walls of the rotor 11 by means of springs 38. As illustrated, a bracket 39 is secured as by bolts 40, FIG. 2, to the external wall of the cylinder 10 and thus provides a guidecoupled by a connecting rod 56 to a shaft 57.

57 is mounted in a fixed position with respect to the end (3 way in which the stop 36 may operate. The springs 3 8 maintain the stop 36 normally in a chamber-closing position. As illustrated in FIG. 1, the end of the stop 36 s provided with a sealing member 45) which preferably is spring-biased into engagement with the external surface of the rotor 11 to maintain an air-tight seal equivalent ,to that maintained in a reciprocating engine by piston rings.

The rotor 11 having a recessed exterior surface 15 provided with an integral stop 110 which serves as a second closure means for the expansion chamber 35. In the form illustrated, stop 11a is integral with and forms a part of the rotor 11. The stop 36 on the other hand is .movable with respect to the housing it} So that it may be retracted to permit passage of the stop 11a at the location of stop 36 upon rotation of rotor 11.

\ As indicated in FIG. 2, a pair of stop lifter rods 44 and 45 extend through bores in a bracket 39 and through the wall of housing 16 into grooves such as grooves 47 in the exterior surface of the rotor 11. The grooves 47 preferably are cam-shaped surfaces encircling rotor 11 at a uniform depth for most of the circumference of rotor ,with the rotor and the other stop is fixed with respect to the housing.

As illustrated in FIG. 1, three cylinders so, 51 and 52 are carried by the rotor 11. The cylinder 56 is shown in section and cylinders 51 and 52. are not sectioned. In cylinder 59 there is positioned a piston 55 whitgl;l is

plates 30 and 31 for the housing 10. The axis of shaft 57 is displaced from the axis 12 of the housing It) and is thus eccentrically located. In a similar manner, a. connecting rod 58 extending from a piston in cylinder 51 is mounted on shaft 57. A connecting rod 59 connected to a piston in cylinder 52 is also mounted on shaft 57. By this means, as the rotor 11 rotates in housing 10 the pistons .in cylinders tt-52 are cyclically reciprocated relative to their respective cylinders by reason of the cc- 7 centric location of shaft 57. Thus any gas in the cylinders may be compressed for injection into the expansion chamber 35.

In the form illustrated, the gases are fed into the respective pistons by way of an injection channel, which is diagrammatically represented by a channel 60, shown only in FIG. 2. The flow path for carbureted combustible mixtures is indicated by arrows 61. The combustible gas mixture is drawn into a given cylinder chamber as the piston goes through a suction stroke by way of a valve in the head of the piston of the form illustrated in the A system of the type illustrated in FIG. 3, combustible gases withinthe housing are drawn into the cylinder and are then ready to undergo a compression stroke.

i As best seen in FIG. 2, the cylinder 50 has controlled openings, such as openings 75, extending upwardly through the ead of the cylinder. The openings are controlled by a valve element 76 which has holes extending therethrough which may be moved into and out of alignment with the holes or channels 75 leading from the cylinder head. When the valve element 76 is in the position illustrated in FIG. 2, gases compressed by the compresion stroke of piston are forced into a combustion chamber 77. In combustion chamber 77 the gases are detonated and simultaneously therewith passages 78 leading upward from chamber 77 and communicating with the expansion chamber 35 are opened by alignment of holes or passages in a second valve element 7 9 with passages 73. At the same time valve element is actuated to close the pasages 75 so that the expansion of gases upon combustion thereof will be effected in the chamber 35 to generate forces between the stops 11a and 36. By this means the tangentially directed forces tend to move stop 11a relative to stop 35, thus producing rotation of the rotor 11.

As seen in FIG. 1, the combustion chamber 77 has a spark plug mounted therein for effecting ignition of the combustible gases. The combustion chamber 77 is provided with a port 81 which leads to a shock chamber 82. As best seen in FIG. 4, the valve element '76 is mounted in a sl-ideway which is preferably wedge-shaped and or" the type illustrated by the wedge-shaped valve 123 of FIG. 5. The wedge-shaped valve is maintained in a gas-tight relationship in the slideway as by seating springs Slots or apertures 75 in the wall of the combustion chamber 77 provide for passage into combustion chamber 77 through the cylinder head. In FIG. 4 the cylinder head has been partially broken away to show at least a portion of the surface of the valve element 76 and the seating springs 83. The valve element 76 has extensions 76:: and 7612 which are adapted to engage the cam surfaces of grooves in the wall or closure elements 3% and 31 of the cylinder to. by this means the valve element 76 is translated cyclically to open and close the ports 75 for injection into the combustion chamber '77 of gases compressed by the piston 5'5.

The shock chamber 82 is a short cylinder in which a piston 82a is normally manned in a position corresponding with the end of a compression stroke by a spring 82b. Upon firing of gases in the combustion chamber 77, the initial shock is absorbed by the spring Upon opening of the port 78 into the expansion chamber 35, the spring 32 then delivers the energy stored therein back into the expanding gaseous atmosphere to propel the rotor relative to the stop 36.

lit will be noted in FIG. 2, that four sealing rings are mounted in the periphery of the rotor 11 and are adapted to contact the interior wall of the bore through housing 10 at axially spaced zones in order to effect a gas-tight seal and thereby prevent escape of gasesfrom the expansion chamber 35. More particularly, the rings, such as ring ss, are mounted in grooves in the periphery of the rotor 11 and are fixed for rotation with rotor 11 pileferably by pins extending into the body of the rotor As shown in FIG. 1, it will be remembered that three cylinders 50, 51 and 52 have been shown. In this arrangement it is provided that as each set of ports leading from a given cylinder passes the location of the fixed stop 36, gases compressed in the cylinder will be injected into the expansion chamber 35 as the chamber grows larger so that there is continually delivered to the expansion chamber energy for propelling the rotor 11 relative to the housing 16. Further, the combustible gases of the mixture are forced into a firing chamber at the peak of each piston stroke. Full mechanical advantage of the forces thus generated are transferred to the expansion chamber 35. As the compressed gases reach or attain higher and higher pressures, the effective arm through which the connecting rod operates because shorter and shorter, thus increasing the mechanical advantage during the compression stroke. At the same time there is utilized or required a minimum of transeral nature as the rotor 11 of FIG. l.

am ss r1 3 lation of parts and thus a minimum of utilization of kinetic energy in stopping and starting the pistons.

As illustrated in FIG. 1, the piston 55 is at the end of its compression stroke. The ports 75 are open and ports 78 are closed. The stop 11a has just passed the stop 36. Stop 36 has been returned to its closed position so that as the rotor moves beyond the point illustrated in FIG. 1 valve 75 will be closed, ports 78 will be opened and the gases in the combustion chamber 77 will be fired to propel the expanding gases through ports 78 into the expansion chamber 35.

As cylinder -1 passes the stop 36, gases in its combustion chamber will be fired and injected into the enlarged expansion chamber 35. 'Finally near the end of the cycle as the cylinder 52 passes the stop 36, gases in its combustion chamber will be injected into the expansion chamber 35.

More particularly, the sequence of operations in the system of FIGS. 1 and 2 for a complete cycle is as follows,

shown in FIG. 1:

( 1) Valve '75 is closed.

(2) As the piston 55 recedes from the top of the cylinder 59, gas is drawn into cylinder 56 by way of valve 61.

(3) After the rotor turns 186, piston 55 starts its compression stroke. Valve 61 closes automatically.

(4) As rotation continues, piston 55 compresses the gas between the piston head and the top of the cylinder until the rotor moves cylinder to about position B, 270 from the stop 36.

(5) At this point the cam-controlled valve 79 closes, it

having been opened from firing a prior charge of combustible gas.

(6) At point A, at about 315 valve 76 opens and the compressed gases are injected from cylinder 5i into the firing chamber 77 as piston completes its compression stroke.

(7) The gases are ignited as stops 11a and 36 pass each other. When stop 36 seats in its closed position, valve 79 is opened. Valve '79 remains open until cylinder Sit reaches point B at 270. It then closes in order to refill firing chamber '77 with unburned gases.

(8) As rotor 11a completes a revolution, the expansion chamber is exhausted through exhaust ports lire into a suitable manifold, not shown.

(9) In the embodiment shown in FIGS. 1 and 2, each cylinder in turn adds more compressed gases to the expansion chamber 35.

chamber which is provided with stops, at least one of which is movable once during each cycle of rotation of the rotor.

It will be appreciated that the relatively simple struc ture illustrated in FIG. 1 may be provided with a plurality of sets of stops such as stop 36, the number equaling the number of pistons and cylinders employed for the compression of gases for use therein. Exhaust ports 1% similarly would be multiplied.

While reciprocating pistons have been employed in the system of FIGS. 1 and 2, the annular expansion chamber itself may be employed for gas compression. A system embodying such action is illustrated in FIGS. 5 and 6.

In FIG. 5 there are two rotor elements and 101 mounted on a common shaft 162 which in turn is journaled in bearings 103 and 104 in the end plates 1% and 196 of the housing 110. Housing is a short cylinder, the ends of which are completely closed by end plates 165 and 196. Each of rotors 1th and 101 is of the same gen- They are characterized by recessed surfaces and are provided with periphti eral contacting elements such as sealing rings 111 to form confined annular Zones between the outer surface of each of the rotors and the inner wall of the housing 110. The rotors 1% and 101 are securely mounted on shaft 102 as by keys 102a. and 10212. In this embodiment of the invention carbureted gas is injected into a first of the annular spaces where it is compressed and then injected from the first space into the second of the annular spaces on the other of the rotors. For example, gas is injected into the Zone 115. Zone 115 has a pair of stops, one of which is carried by rotor 1551 and the other of which, the stop 116, is mounted in the wall of housing 11% and is adapted to be moved into and out of engagement with the rotor 191 to provide a selective closure means therefor. Gas is compressed in the zone or chamber 115 and is then fed upward through openings in housing 1-10 and into a manifold structure 12 Gas in the manifold 12% then passes through a valve unit :121 into a combustion chamber 122. The expanding gas is then permitted to pass through a valve structure 123 into the left end of the manifold and then through ports down into the second chamber 124. The expanding gases in chamber 124 then react between a fixed stop carried by the rotor 16 i and a movable stop similar to stop 116 (but not shown in FIG. 5) to drive the rotor under the influence of the expanding gases. From zone 124 spent gases are exhausted from the motor unit.

The combustion chamber is provided with a spark plug 125. A shock chamber 126 communicating by way of port 127 with the combustion chamber 122 is provided for operation of the type generally above described in connected with FIGS. 1 and 2.

In this embodiment of the invention the stops, such as 116, are moved in and out of engagement with the respective rotors, i.e., rotor M1, by means such as a cam follower 131 which is mounted on a shaft 131 which in turn is carried by a litter arm 132. Lifter arm 13-2 includes a yoke 133 which is coupled to the stop \1 16 as by an arm 134. A cam track 135 formed on the inner surface of the rotor 181 mates with the cam follower 1341 to provide the desired motion of the stop 116.

Referring now to FIG. 6, a top View of the double rotor system of FIG. 5 is illustrated. The sectional view is taken through the manifold 124 of FIG. 5. Gas from a carburetor is fed into the system by means of the flow channel 141 The combustible gas then enters the compression chamber 115 of :FIG. 5 through ports 14 1 of FIG. 6 which are inside the manifold housing 12tla. The combustible gas is then compressed as the stops fixed on the rotors associated with the rotor 101 of FIG. 5 rotate toward the retractible stops in the housing 211%. The compressed gases are forced out of the chamber 115 by way of ports 1 12 and into the enclosure formed by the manifold 12th. Gases then travel through ports 143 in the valve element 1 .4 and into a combustion chamber 122. A pair of spark plugs 125 and 125a are mounted in the wall of the combustion chamber 122. The compressed gases in chamber 122 are ignited and travel through a valve element into a second chamber of manifold 120 and thence downwardly through ports in the wall of the housing 110 into the chamber 124 of FIG. 5. The expanding gases in the chamber 124 then develop forces between the fixed and movable stop which close the chamber, thus driving the rotor 1% thereby utilizing the energy developed upon the expansion of the gases. Both rotor 1:10 and 101 being mounted securely on shaft 102, rotate together. Thus there is developed the power necessary for the compression of the gases injected into the chamber 115.

Valves 1 4 and 145 are the type illustrated in FIG. 7. FIG. 7 is a partial sectional view of FIG. 6 taken along the lines 7-7 of FIG. 6. The valve element 144 is a wedge-shaped bar having a pair of ports 144a extending therethrough which are adapted to be moved into registration with ports such as port 122:: extending between the manifold 121] and the combustion chamber 122. Valve element 144 is maintained in a sealed position by springs 3 such as springs 14411 which develop a force between the housing 120 and a rider bar 144a As seen in FIG. 6 the valve element 144 is moved to position the apertures 144:: by means of a cam 150. Cam 156 is mounted on a shaft 151 which is journaled in bearings 152 and 153 and in turn is coupled by means of a gear train 154-155 to the shaft 102 so that the valve clement 14-4 will be moved in synchronism with the rotors 1% and 161 of FIG. 5. In a similar manner the valve element 145 is moved under the control of a cam 156 which is geared by way of shaft 15? and gear train 153, 159 to shaft 1452.

Expanding gases which enter the chamber 124, FIG. 5, by way of ports 1 36, FIG. 6, are exhausted by way of ports 1 27 and an exhaust channel 148 in the wall of the manifold 12%.

As illustrated in FIG. 6, the movable stop 116 is mounted for movement into and out of engagement with the walls of the rotor 101. Similarly, a movable stop 161i is adapted to be moved into and out of engagement with the walls of the rotor 1%. Thus in the embodiment of FIGS. 5-7 a pair of rotors are provided one of which serves as a compression unit and the other of which serves as a firing or expansion unit in order to compress gases and utilize energy in a combustible expanding gas mixture for developing a rotational force.

The operational cycle of the system of FIG. 5 and FIG. 6 is as follows:

(1) Shaft 192 rotates in a clockwise direction as viewed from the right-hand end, PEG. 6. Stops 115 and 160 for expansion chamber 124 pass their respective rotor stops at the same instant.

(2) After the stops pass each other, stops 116 and res seat in their closed positions on the rotor.

(at) A vacuum is formed behind the movable stop 116 in the compression chamber 115. Thus carbureted gases are sucked into the chamber 115. On the next revolution, these gases are compressed in front of the rotor stop while additional gas is being sucked into the cylinder behind the rotor stop. Thus intake and a compression stroke are completed on each revolution of the rotor.

(3) On the expansion side a power and an exhaust stroke are completed on each revolution of the rotor in like manner.

(4) Timing.

(a) Valve 123 closes at about 265 of the rotor stop relative to the stop 116 in order to get the firing chamber ready to receive carbureted gases.

([2) Valve 121 opens at about 275 and the compressed gases flow into the firing chamber.

(0) Valve 121 closes just before stop 116 breaks seal with the rotor 111.

(d) Gas in firing chamber 12?. is detonated as stops pass each other.

(e) Stops 115 and res fall into closed position and valve 123 opens.

In a further embodiment of the invention illustrated in FIG. 8, a reciprocating piston 200 is employed for compressing gases in a cylinder 2431 which gases are then injected through a valve port 204 to an expansion chamber between a fixed stop 2% on rotor 22% and a movable stop 207 mounted in wall 2%. The stop 207 is moved into and out of engagement with the walls of the expansion chamber by way of a linkage including a cam follower 210 mounted on an arm 211 which in turn is engaged by a yoke 212 pivoted for rotation about an axis 213 and coupled by pin 21 1 to the upper end of the movable stop 267. A spring 215 serves to urge the yoke 212 outward and thus maintain the stop 2117 in engagement with the cam surface of the rotor 2:16. Cam follower 21% passing over the cam actuating portion 221) serves to lift stop 297 to permit the fixed stop 2&5 to

pass stop 237. In this embodiment of the invention the central shaft 221 is coupled by way of a suitable linkage, such as a belt 222, to a shaft 223, which is a crankshaft on which there is mounted a connecting rod 224. Connecting rod 224 is coupled to the piston 200 in cylinder Zill. Shaft 223 is also coupl d by way of a belt linkage 225 to a pulley 226 to rotate a valve actuating cam 227. A spark plug (not shown) located in the combustion chamber 2% serves to detonate the gases therein for expansion through the port 204 into the expansion chamber between stops 265 and 207. Thus by employing the fixed and movable stops in connection with an expansion chamber extending around the periphery of a rotating element, there may be utilized the advantages found in turbine type motors at the same time the efficiency of internal combustion reciprocating engines is maintained.

In FIG. 9 there is illustrated a modification of the system of FIG. 8 which includes a pair of compression chambers 2d3a and 2-tl3b. The latter chambers correspond with chambers 7.03 of FIG. 8. Spark plugs 230 and 231 are provided for alternately firing gas charges injected and stored in the two compression chambers. Valve ports 264a and 294i) lead from chambers 263a and ZtlSb, respectively, into the expansion chamber 2%:2 between the fixed stop on rotor 2% and a movable stop (not shown in FIG. 9) mounted in the wall 2%. Valves 232 and 233 serve to close ports 2 14a and 20415, respectively, leading into the chamber 206a. Valve unit 282a is employed for controlling flow of compressed gases under action of the pistonZtlt) alternately into the chambers 263a and 2il3b. Ports in valve 2tl2a are adapted alternately to be brought into alignment with ports 261a and 2611) in the head of the cylinder 231. In operation during a first cycle a gas mixture in cylinder 291 passes through port Zilla and valve 292a into compression chamber On the succeeding intake cycle of piston 2%, valve 2112a is moved to close port 201a. Upon closure, spark plug 239 is energized to fire the gas mixture and at the same time valve 232 is lifted so that the expanding gases go into chamber 2116a. The force of such gases may then be utilized for substantially the entire cycle of rotor 2%. During this time interval, on the next compression stroke of piston 291), the mixture is forced hrough port 291!) and valve 292a into chamber As the stop 2&5, FIG. 8, passes Stop 26?, valve 202a closes port 231a, 201b, spark plug 231 is energized and valve 233 is lifted so that the expanding gases pass into chamber Ztl'a.

In more detail, this sequence of operation is as follows:

(1) Valve 231 has three positions.

((1) Ports Zilla only open when valve 21120 is in the lefthand position.

(1)) Ports 2111b only open when valve 202a is in the righthand position.

(0) Ports 2111a and 2131!; close when valve 202a is in mid-position.

(2) Shafts 223 and 221, FIG. 8, are connected by belt 22-2 in a 1:1 ration in such a manner that when piston 2% is at the top of cylinder 201, the two stops 2G7 and 2 15 are in passing positions.

(3) Timing.

(a) As piston 200 starts its intake stroke, ports 201a and 201]) are closed. Carbureted gases are drawn into cylinder Zlll by Way of a valve (not shown) but which may be (i) A lay-pass valve as common in a two-cycle engine;

(ii) A butterfly valve as in top of piston 200, FIG.

(iii) A butterfly valve but located in the top of cylinder 201.

(b) As piston 200 finishes its intake stroke and starts its compression stroke (i) An intake valve (not shown) closes;

(ii) Ports 201a opens;

(iii) Valve 232 is closed.

(c) As piston 200 finishes its compression stroke and starts another intake stroke;

(i) Ports 201a and 20th are closed;

(ii) Chamber 203a fires and expanding gases are held in the firing chamber and shock chamber until;

(iii) Stop 207 (FIG. 8) goes into closed position.

(iv) Valve 232 opens and expanding gases drive stop Z away from stop 207 thus rotating rotor 206.

(v) Valve 232 stays open until stop 2% has passed exhaust ports 228.

In the meantime piston 200 has completed another intake stroke and almost another compression stroke to compress the carbureted gases into chamber 203b, which gas is fired in the same manner as gas in chamber 203a. Thus alternating firing takes place in chamber 203a and 2031).

When the invention has been described in connection with engines utilizing the energy in expanding gas mixtures following detonation thereof, it is to be understood that the invention may be employed to utilize energy from steam, compressed air or other compressed gases such as may be employed in driving hand hools and the like. Furthermore, units of the type disclosed may be stacked as to be used in combination to form multiunit systems of increased power capacity. The features involved include a rotor in a cylindrical housing where the housing and/or the rotor are suitably shaped to form a sealed expansion chamber in which provision is made for a pair of stops, one of which moves with the rotor and the other of which is fixed with the housing to provide a closed expansion chamber comprising a part of an annular chamber within the housing. The closed expansion chamber increases in dimension under forces developed from energ in the expandable gases. Thus there are employed desirable features of engines both of the internal combustion type and of the turbine type.

Having described the invention in connection with certain embodiments thereof, it is understood that further modifications may suggest themselves to those skilled in the art and it is intended to cover such modifications as fall within the scope of the appended claims.

What is claimed is:

1. An engine for developing powered rotation from the energy of expanding gases which comprises a cylindrical housing having an exhaust port therein, a rotor mounted for rotation coaxially within said housing and having axially spaced circumferential segments thereof contacting the inner walls of said housing to form spaced sliding closures therewith to form with the walls of said housing an annular chamber, a fixed stop forming a part of said rotor extending across said chamber, a movable stop mounted on said housing adjacent said exhaust port and forming a lateral closure for said chamber, means for retracting said movable stop to permit the stops to pass one another upon rotation of said rotor, at least one cyiindenpiston combination mounted in said rotor for compressing a combustible gas mixture during each cycle of said rotor, means for detonating said gas mixture for developing high pressures, valve means carried by said rotor for injecting the detonated gas mixture into said chamber between said stops immediately after passage thereof in each cycle of rotation for developing a tan gentially directed force between said stops.

2. An engine for developing powered rotation from energy of expanding gases which comprises a cylindrical frame structure having an exhaust port therein, a rotor mounted for rotation coaxially within said frame structure and forming a stopped annular expansion chamber with said frame structure, at least one cylinder-piston combination mounted in said rotor, a linkage between said piston and said frame structure eccentric with respect to the axis of said rotor for controlling positional variation of said piston in said cylinder during rotation of said rotor, structure forming a combustion chamber communieating between said cylinder and said expansion chamber, means for injecting into said combustion chamber a combustible gas mixture cyclically in synchronism with rotation of said rotor, means for detonating said gas mixture when under compression by said piston for developing high pressures, and valve means cam-actuated at the ends of said rotor carried by said rotor for connecting said cylinder to said expansion chamber at. the end of each compression stroke of said piston.

3. An engine for developing powered rotation from energy of expanding gases which comprises a cylindrical housing having an exhaust port therein, a rotor mounted for rotation coaxially within said housing and forming with said housing a stopped annular expansion chamber, a plurality of cylinder-piston combinations mounted in said rotor, a linkage between each said piston and said housing eccentric with respect to the axis of. said rotor for variably positioning the pistons in the cylinders during rotation of said rotor, structure forming a combustion chamber communicating between each said cylinder and said expansion chamber, means for injecting into said combustion chambers combustible gas mixtures cyclically in synchronism with rotation of said rotor, means for detonating said gas mixtures when under compression by said pistons for developing high pressures, and valve means cam-actuated at the ends of said rotor carried by said rotor for conducting said detonated gases from each combustion chamber to said expansion chamber at the end of each compression stroke of said pistons.

References Cited by the Examiner UNITED STATES PATENTS 765,047 7/04 Shumway 12314 993,960 5/11 Carroll 123--14 1,309,735 7/19 Henig 123-14 1,602,018 10/26 Harvey.

, 3,040,530 6/62 Yalnizyan 60-39.61

SAMUEL LEVINE, Primary Examiner.

RALPH H. BRAUNER, KARL J. ALBRECHT,

ABRAM BLUM, Examiners. 

1. AN ENGINE FOR DEVELOPING POWERED ROTATION FROM THE ENERGY OF EXPANDING GASES WHICH COMPRISES A CYLINDRICAL HOUSING HAVING AN EXHAUST PORT THEREIN, A ROTOR MOUNTED FOR ROTATION COAXIALLY WITHIN SAID HOUSING AND HAVING AXIALLY SPACED CIRCUMFERENTIALLY SEGMENTS THEREOF CONTACTING THE INNER WALLS OF SAID HOUSING TO FORM SPACED SLIDING CLOSURES THEREWITH TO FORM WITH THE WALLS OF SAID HOUSING AN ANNULAR CHAMBER, A FIXES STOP FORMING A PART OF SAID ROTOR EXTENDING ACROSS SAID CHAMEBR, A MOVABLE STOP MOUNTED ON SAID HOUSING ADJACENT SAID EXHAUST PORT AND FORMING A LATERAL CLOSURE FOR SAID CHAMBER, MEANS FOR RETRACTING SAID MOVABLE STOP TO PERMIT THE STOPS TO PASS ONE ANOTHER UPON ROTATION OF SID ROTOR, AT LEAST ONE CYLINDER-PISTON COMBINATION MOUNTED IN SAID ROTOR FOR COMPRESSING A COMBUSTIBLE GAS MIXTURE DURING EACH CYCLE OF SAID ROTOR, MEANS FOR DETONATING SAID GAS MIXTURE FOR DEVELOPING HIGH PRESSURES, VALVE MEANS CARRIED BY SAID CHAMBER BETWEEN SAID STOP IMMEDIATELY AFTER PASSAGE THEREOF IN EACH CYCLE OF ROTATION FOR DEVELOPING A TANGENTIALLY DIRECTED FORCE BETWEEN SAID STOPS. 